Distributor



E. C CAMPBELL ETAL DISTRIBUTOR July 24, 1962 3,045,458

Filed April 27, 1960 2 Sheets-Sheet l INVENTORS Edgar C. Campbell y Fred E Tlmpner Their Aiforney July 24, 1962 E. cv CAMPBELL ETAL 3,045,458

DISTRIBUTOR Filed April 27, 1960 2 Sheets-Sheet 2 IN VEN T ORS Fig, 4 Edgar 0. Campbell 4 BY FredE Timpner QRWW Their Afforney Filed Apr. 27, 196% Set. No.'25,'076 13 (Ilaims. (Cl. 64-25) This invention relates. to distributors and more particularly to distributors that are provided with apparatus for cancelling out the eifects of rapid acceleration and deceleration of the distributor shaft.

In presently used distributors, it has been common practice to employ a centrifugal advance mechanism including weights that are pivoted to a plate and which react on a member connected with a distributor shaft for varying the angular relationship of the cam and shaft in accordance with engine speed. This arrangement has beensatisfactory in operation where rigid drive: lines are connected to the engine.

With the advent of torsion bar drive lines connected with the engine (which are subjected to the effects of tor-- sional vibrations in. the drive shaft) a new situation is presented in that it is possible. to obtain instantaneous accelerations as high as one million, nine hundred and twenty thousand, r.p.rn. per minute. The presence of these ac celerations and. decelerations transmitted through the timing train can create forces on the distributor parts that adversely influence spark distribution.

Itis accordingly an object of this invention to provide a distributor with means for preventing rapid acceleration and deceleration from adversely influencing the performanee of the distributor.

Another object of this invention is to: provide the centrifugal advance mechanism of a distributor with an inertia ring that is effective to cancel out acceleration forces applied to the shaft of the distributor.

A more specific object of this invention is to provide a distributor apparatus wherein an-inertia ring is secured by linkage to the distributor cam plate assembly whereby rapid accelerations of the distributor shaft are prevented from adversely influencing. the performance of the distributor.

Further objects andadvantages of the present invention will be apparent from the following description reference being had to the accompanying drawings wherein preferred embodiments of the present invention are clearly shown.

In the drawings:

FIGURE 1 is a side view-with parts broken away and partly in section illustrating a distributor made in accordance with this invention.

FIGURE 2 is a view taken along line 22 of FIG- URE 1.

FIGURE 3 is a view taken along line 33 of FIG- URE l.

FIGURE 4 is an exploded view of certain parts of a distributor madelin accordance with this invention.

Referring now to the drawings and more particularly to FIGURE-1, the distributor of this invention includes a cast metal base. member generally designated by referencenumeral which has asuitable central opening receiving a shaft 12. The shaft 12 is adapted to be connected withthe' timing mechanism of an internal combustion engineand is-journalled for rotation within the base member 10 by meansof bearings not shown. Journalled for rot tion on the shaft 12 is, a cam plate assembly which is generally designated byreference numeral 14. This cam plate assembly is better illustrated in the ex.- ploded view of FIGURE ,4-and it is seen that it includes a port-ionl6 embracing the top endofthe shaft 12 and $345,453 Patented. July 24, 1962 a cam portion 18. The cam portion, as is Well-known to those. skilled in the art, is used to engage the rubbing block of a set of breaker points of a distributor (not illustrated) for controlling the opening and closing of the breaker points of the distributor. The cam plate member 14 further includes an annular disk like member 20 which carries the posts 22, 24 and 26. The disk-like member 20 has a slot 28 and has threaded openings 30 and 32. In" addition, the disk-like member 20 is provided with the opening 36, the. purpose of which will be more fully described hereinafter. The disk-like member 20 also carries downwardly projecting posts designated by. reference numeral 4t The distributor of this invention further includes an assembly which is generally designated by reference numeral 42. This assembly includes the spider member 44 which carries posts 46 and 47. The spider member 44 also carries downwardly projecting posts 48 each of which carries a part formed of a plastic bearing material which is designated by reference numeral 50. The spider member has a slot 51 and is secured to the distributor shaft 12. It can be seen from FiGURE 1 that the assembly 42 also includes an advance plate 52 which is welded to the shaft 12 and also to the spider 44. It can be'seen from FIGURE 1 that the pins 46 and 47 pass through the spider 44 and also through the advance plate 52.

The distributor in addition to the parts heretofore described, includes weight members 53, each having an opening 54. An inertia ring generally designated by reference numeral 55 is provided which is formed of metal material and which has three downwardly projecting pins or lugs 56.

Referring now more particularly to FIGURES 1, 2,

and 3, it is seen that the cam plate assembly 14 is journalled for rotation with respect to the shaft 12, this assembly being supported at its lower end by the base 10 or by a suitable bearing extending upwardly from the base 10. It is seen that the pin 22 which extends upwardly from the plate member 20 passes through one of the openings 54 in a weight member 53 so that one weight member is pivoted thereon. It is also seen that the pin 22 is connected with pin. 47 by a spring 58. It can be seen that the pin 47 passes through the advance plate 52 and also passes through the spider plate 44. The lower end of the pin 4-7 swings within the slot 28 formed in the plate 24) of the cam plate assembly 14.

The pin 26 which is attached to the plate member 20 extends upwardly through an opening 51 formed in spider member 44 and it is seen that one of the weight members 53 is journalled for rotation on the pin or post 26. The post 26 is connected with the post 46 by a spring 60. The post 46, as is clearly apparent from FIGURE 1, passes through the plate 44.

It can be seen from FIGURES 1, 2, and 3 that the downwardly-extending posts 56 of the inertia ring are fitted within slots 62 formed in the link members'64. There are three link members as is clearly apparent from an inspection of FIGURE 3 and it is seen that each post 56 of the inertia ring 55 extends down into a slot 62 formed respectively in each link member. The lower end of the posts 56 are fitted with snap rings which slide on the lower surfaces of the links-64 thus preventing the posts 56 from moving out of the slots 62.

The links 64 are pivotally mounted on the posts 48- the plate member 44 whereas the lower edge of the bear- The link members 64 are also secured to the pins 40 which extend downwardly from the plate 20 of cam plate assembly 14. The pins 40 are positioned Within slots 68 formed in the link members 64. The pins 40 like the pins 48 and 56 are formed with grooves at their lower ends which receive snap rings shovm in FIGURE 1 for preventing the pins from leaving the slots.

A rotor member generally designated by reference numeral 70 is provided which carries a contact 72 cooperating with the central terminal 74 of a distributor cap generally designated by reference numeral 76. It can be seen that the distributor, cap 74 is secured to the base member by the spring finger fasteners 78.

The rotor member 70 is formed of the usual insulating material and has an electrical contact in addition to the contact 72 which applies spark impulses to the spark plugs of an engine through the distributor cap as the rotor 70 rotates. The rotor 70 rotates with the disk member 20 of the cam plate assembly 14 and is secured thereto by screws 80 which are threaded into the openings 30 and 32 formed in the plate member 2t). The rotor 7% has an integral, downwardly extending boss 82 which fits within the opening 36 formed in the plate member 20. The pin 24 extending upwardly from the plate member 20 fits within a suitable opening formed in the rotor member 70 and it is thus seen that the screws 80, the boss member 82 and the pin member 24 serve to provide a tight connection between the rotor 70 and the plate member 20 so that they rotate in unison.

In carrying forward this invention, the inertia of the inertia ring 55 is made so that it is equal to the inertia of the cam plate assembly 14, the weights 53 and the rotor 70, or, in other words, all the parts of the centrifugal advance mechanism at a given speed. It has been found, however, that even though the inertia ring 55 has an inertia that is slightly less or slightly greater than these parts, the inertia ring still serves to prevent spark scatter and to improve the performance of the distributor. It thus is seen that any effects of acceleration or decleration of the distributor shaft will not be felt by the cam plate parts where an inertia ring is provided. This is the result of the inertia ring reacting through the linkage in a manner opposite to the reaction of the cam plate, and thus, cancelling it out. At constant speed, the inertia ring will have no effect.

In order to better understand the effect of the inertia ring 55 on the operation of the distributor, reference should be had to FIGURE 3. It can be seen that if the cam plate member 20 is being rotated in a counter-clockwise direction as viewed in FIGURE 3, the weights 53 will be thrown outward to adjust the plate member 20 relative to the shaft 12. Under ordinary conditions, the outward movement of the weights 53 advances the position of the cam 18 relative to the shaft to advance spark timing. Where the shaft is subjected to sudden acceleration or deceleration in the order of that mentioned above, the centrifugal advance mechanism of the distributor may produce erroneous results.

As an example, if the shaft 12 and plate 20 are ro-, tating in a counter clockwise direction in FIGURE 3 and the shaft is suddenly accelerated, the net effect is to retard the spark rather than advance it. This is just the opposite effect of which is desired. On the other hand where the shaft 12 is suddenly decelerated, the plate 20 because of inertia effects will overcome the effects of the springs and weights so that the spark is advanced rather than being retarded. This again is just opposite to that which is desired.

The inertia weight 55 will apply forces to the plate 20 to overcome the inertia effects of the plate 20 and its attached parts during sudden acceleration or decleration. Under steady state running, that is, steady engine speed ing members are in engagement with the link members bly 14 is rotated.

or constant angular velocity of the shaft 12, the centrifugal weights 53 are thrown out in the usual manner to cause the plate 20 to advance. Since there now is steady state conditions, there are no inertia forces involved, and the distributor responds in the same manner as a distributor that does not have an inertia weight 55.

Where the inertia ring 55 has a larger polar inertia than the sum of the inertias of the plate 20 and its attached parts and where the shaft 12 is suddenly accelerated, the inertia ring 55 plays a vital role in cancelling the detrimental effects of inertia forces of the plate 20 and its attached parts. During this acceleration, the inertia ring 55. offers greater resistance than the plate 20 and its attached parts. The force at the outer pins 56 of links 64 will be greater than that at the inner pins 40 which causes a force couple to be developed about the pins 48. This force couple advances the plate 20 in relation to the shaft 12 and thus cancels out the inertia effects of the plate 20 due to sudden acceleration of the shaft 12.

In the case of a decelerating shaft 12 with the inertia of plate 20 and its attached parts, the same as just described above, the inertia ring 55 will be more reluctant to slow down causing a force couple in the reverse direction on the links 64 to retard the spark. In this case, the spring force from the springs will assist the inertia forces in retarding the plate 20. The centrifugal weights will be attempting to advance the spark. I

If the inertia of the inertia ring 55 is less than that of the plate 20 and its attached parts, the distributor will act substantially in the same manner as though the ring were not there. In this instance, the ring only serves to reduce the effect of the inertia of the inner plate 20. If the inertia of the ring 55 and the plate 20 and its attached parts are substantially equal, the forces developed at pins 40 and 56 will be equal. This will eliminate any movement of the plate 20 in relation to the shaft 12 other than that caused by the weights 53.

It can be seen that the links 64 in each instance provide force couples on pins 40 and 56 which vary under accelerating and decelerating conditions. These force couples are due to the inertia of the ring 55. and prevent the distributor from exhibiting erroneous characteristics during sudden acceleration and deceleration of the shaft 12. If the inertia ring were not provided, the sudden accelerations and decelerations could cause an advance of the spark when a retarding is required and a retarding of the spark when an advance is called for.

It will be appreciated that the weight members 54 still provide the required centrifugal advance in that they react against the advance plate 52 as the cam plate assem- It thus is seen that the distributor of this invention provides the required centrifugal advance, but in addition, compensates or cancels out the effects of rapid acceleration or deceleration of the shaft 12.

While the embodiments of the present invention as herein disclosed, constitute preferred forms, it is to be understood that other forms might be adopted.

What is claimed is as follows:

1. A distributor comprising, a rotatable shaft adapted to be connected with an engine, a cam plate assembly rotatable with respect to said shaft and including a cam member and first and second weight members, an advance plate secured to said shaft and cooperating with said weights for controlling the angular relationship between said cam member and said shaft, and means connected with said cam plate assembly for at least partially cancelling out the inertia effects of said cam plate assembly due to rapid changes in motion of said shaft, said last named means including a third weight member.

2. A distributor comprising, a base member, a shaft journalled for rotation in said base member, a cam plate assembly rotatable with respect to said shaft and including a cam member and a plate member, centrifugal weight means pivotally supported by said plate member, an ad.

vance plate secured to said shaft and cooperating with said centrifugal weight means, and means including an annular weight member connected with said plate member for at least partially cancelling out the inertia effects of said cam plate assembly due to rapid acceleration and deceleration of said shaft.

3. A distributor comprising, a shaft, a cam plate assembly rotatable with respect to said shaft and including a cam member and a plate member, a pair of weights located on one side of said plate member and pivoted thereto, an advance plate secured to said shaft and cooperating with said weights, an annular weight member, and a plurality of pivotally mounted links connecting said plate member with said annular weight member.

4. A distributor comprising, a shaft, a cam plate assembly rotatable with respect to said shaft and including a cam member and a plate member, a pair of weights pivotally supported by said plate member, an advance plate member secured to said shaft and cooperating with said weight members to vary the angular relationship between said shaft and cam member, a rotor member secured to said plate member, and means connected to said plate member for cancelling out the effects of rapid acceleration and deceleration of said shaft.

5. A distributor comprising, a shaft, a cam plate assembly rotatable with respect to said shaft and including a cam member and a plate member, a pair of pins supported by said plate member, weight members pivoted to said pins, an advance plate member secured to said shaft having a pair of pins, spring means connected between the pins of said advance plate member and said plate member, said weight members cooperating with said advance plate member to vary the angular relationship between said cam member and said shaft as a function of speed of said shaft, and an inertia ring connected with said plate member.

6. A distributor comprising, a shaft, a cam plate assemblyrotatable with respect to said shaft including a cam member and a cam plate member, a pair of 'weight members pivotally supported by said cam plate member, an advance plate cooperating with said weight members for varying the angular relationship of said cam member and said shaft in response to speed of rotation of said shaft, an inertia ring, and a plurality of links connecting said inertia ring and said cam plate member, said links having a slidable connection with both said cam plate member and said inertia ring.

7. A distributor comprising, a base member, a shaft journalled for rotation with respect to said base member, a cam plate assembly rotatable with respect to said shaft and including a cam member encircling said shaft and a cam plate member, a pair of weights pivotally supported by said cam plate member, an advance plate secured to said shaft and cooperating with said weights for varying the. angular relationship between said cam member anu said shaft in accordance with the speed of rotation of said shaft, a spider member secured to said shaft, a plurality of links pivotally supported by said spider member, and means connecting opposite ends of said links with said cam plate member and with said inertia ring.

8. A distributor comprising, a base member, a shaft journalled for rotation with respect to said base member, a cam plate assembly rotatable with respect to said shaft and including a cam member encircling said shaft and a cam plate member, a pair of weight members pivotally supported by said cam plate member, an advance plate member secured to said shaft and rotatable therewith, said advance plate member and said Weight members cooperating to angularly adjust said cam member relative to said shaft in accordance with the speed of rotation of said shaft, a spider member secured to said shaft and rotatable therewith, a plurality of depending pins carried by said spider member, a link member pivotally connected to each of the pins carried by said spider member, an inertia ring, and pin and slot connections connecting said cam plate memher and said inertia ring with said links.

9. A distributor comprising, a base member, a shaft journalled for rotation with respect to said base member, a cam plate assembly rotatable with respect to said shaft including a cam member and a cam plate member, an advance plate member secured to said shaft and rotatable therewith, a pair of weights pivotally supported by said cam plate member and engageable with said advance plate member for angularly adjusting said cam member with respect to said shaft, a spider member secured to said shaft and rotatable therewith, a rotor connected to and rotatable with said cam plate member, an inertia ring, and means including a plurality of link carried by said spider member connecting said inertia ring and said cam plate member.

10. In a distributor, the combination comprising, a shaft, a cam plate assembly rotatable with respect to said shaft and including a cam member, means secured to said cam plate assembly including pivotally supported weight means for adjusting said cam member angularly with respect to said shaft in accordance with the speed of rotation of said shaft, and means connected with said cam plate assembly for cancelling out the effects of rapid acceleration and deceleration of said shaft.

11. Apparatus of the type described comprising, rotatable shaft means, a member adjustable relative to said shaft means, control means responsive to the speed of rotation of said shaft means for adjusting said member relative to said shaft means, and means for at least partially cancelling out the inertia effects of said member and control means due to sudden acceleration or deceleration of said shaft means, said last named means including an inertia weight driven by said shaft means.

12. Apparatus of the type described comprising, rotatable shaft means, a member adjustable relative to said shaft means, means responsive to the speed of rotation of said shaft means for adjusting said member relative to said shaft means, force transmitting link means, driving means connected with said shaft means for-driving said link means, said link means being shiftable relative to said driving means, an inertia member, and means connecting said link means with said member and with said inertia member.

13. Apparatus of the type described comprising, rotatable shaft means, a control member adjustable relative to said shaft means, means responsive to the speed of rotation of said shaft means for adjusting said control member relative to said shaft means, force transmitting link means, driving means connected with said shaft means for driving said link means, said link means being pivoted between its ends to said driving means, an inertia member, and means connecting spaced points of said link means, which are located at opposite sides of the pivot between said link means and driving member, respectively with said inertia member and control member.

References Cited in the file of this patent UNITED STATES PATENTS 2,215,301 Schneider Sept. 17, 1940 2,421,873 Forsyth June 10, 1947 2,472,181 Worth June 7, 1949 2,977,778 Backlund et al. Apr. 4, 1 961 

